KR20150006366A - Double damping flywheel with improved damping means - Google Patents

Double damping flywheel with improved damping means Download PDF

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Publication number
KR20150006366A
KR20150006366A KR1020140083683A KR20140083683A KR20150006366A KR 20150006366 A KR20150006366 A KR 20150006366A KR 1020140083683 A KR1020140083683 A KR 1020140083683A KR 20140083683 A KR20140083683 A KR 20140083683A KR 20150006366 A KR20150006366 A KR 20150006366A
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KR
South Korea
Prior art keywords
flywheel
inertia
inertia flywheel
17b
thin plates
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Application number
KR1020140083683A
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Korean (ko)
Inventor
카를로스 로페즈-페레즈
Original Assignee
발레오 앙브라이아쥐
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Priority to FR1356687 priority Critical
Priority to FR1356687A priority patent/FR3008152B1/en
Application filed by 발레오 앙브라이아쥐 filed Critical 발레오 앙브라이아쥐
Publication of KR20150006366A publication Critical patent/KR20150006366A/en

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/131Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
    • F16F15/133Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
    • F16F15/1333Spiral springs, e.g. lying in one plane, around axis of rotation
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/131Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
    • F16F15/133Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
    • F16F15/1336Leaf springs, e.g. radially extending
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2230/00Purpose; Design features
    • F16F2230/0052Physically guiding or influencing
    • F16F2230/0064Physically guiding or influencing using a cam

Abstract

The present invention relates to a double damping flywheel with an improved damping means which has improved performance and/or is simply manufactured and assembled. The double damping flywheel of the present invention comprises a damping means including: a first inertia flywheel (2) and a second inertia flywheel (3) designed to be fixated on the end of a crank axis performing rotational movement with respect to each other near a rotary axis (X); and friction means (24, 25, 26) arranged between a first inertia flywheel (2) and a second inertia flywheel (3) to apply a frictional resistance torque during the angular displacement between the first inertia flywheel (2) and the second inertia flywheel (3), as a damping means to transmit a torque between the first inertia flywheel (2) and the second inertia flywheel (3); and to damp rotational aperiodicity.

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a double damping flywheel having improved damping means,

The present invention relates to automotive transmissions, and more particularly to the field of dual damping flywheels.

The dual damping flywheel (DDF) includes a coaxial first inertial flywheel and a second inertial flywheel, which rotate relative to each other by a bearing, such as a ball bearing. The first inertia flywheel is designed to be fixed to the crankshaft of the internal combustion engine. The second inertia flywheel generally forms a reaction plate designed to cooperate with the friction disc of the clutch. The first flywheel and the second flywheel are rotationally connected by a damping means that transmits torque and can damp rotational irregularity. The damping means is a bent helical spring, which is generally circumferentially disposed in a hermetically sealed annular chamber formed in the first flywheel and filled with lubricant. The spiral spring is supported on the radial leg of the annular blade fixed at its end on the projection of the side wall of the annular chamber and by the rivet on the second flywheel. This allows all rotations of one of the flywheels to cause compression of the spring in one direction or another, thereby applying a restoring force to return the elements toward their relative non-stationary position.

The stiffness of such a damping device is determined by the number of helical springs constituting it, the inherent rigidity of the springs, and the installation diameter of the springs. The choice of stiffness of such a torsional damping device is obtained by a balance between the non-periodic filtering efficiency which increases when the stiffness decreases and the capacity to deliver the maximum engine torque without the helical layers of the spring abutting against each other Loses.

In order to improve the vibration filtering performance at a weak torque, it is known to provide a torsional damping device in which the characteristic curve of the transmission torque according to the angular displacement has a plurality of slopes. Thus, at low torque, the stiffness of the damping device is smaller, while the stiffness of the torsional damping device is greater if the transmitted engine torque is close to the maximum. However, the stiffness change zone causes discontinuity and shock, which impairs the acyclic damping characteristics.

On the other hand, helical springs are extremely sensitive to centrifugal forces when placed in the circumferential direction. Also, the first flywheel holds it radially to prevent the spring from springing out. However, these radial holding means induce collateral friction which affects the damping function by blocking the spring when the rotational speed is too high. It is certainly anticipated that by providing complex shapes, surface treatments or lubricant introduction, this collateral frictional effect will be reduced. However, these measures complicate the fabrication of dual damping flywheels and are not entirely satisfactory.

In addition, limiting the volume assigned to the helical spring limits the angular displacement between the first inertial flywheel and the second inertial flywheel, so that the helical spring has a relatively large stiffness for optimal filtering of the aperiodic.

Finally, because the helical springs are relatively disturbed in the axial direction, the axial dimensions of the first and second flywheels are sometimes down-dimensioned, due to the given axial charge volume. However, this downward dimensioning causes difficulty in removing the mechanical durability problem and the heat generated by friction of the clutch disc with respect to the second inertia flywheel.

Thus, dual damping flywheels with helical springs are not entirely satisfactory.

The present invention aims to solve these problems by proposing a dual damping flywheel whose performance is improved and / or its fabrication and assembly are simple.

To this end, according to a first aspect of the present invention,

A first inertia flywheel, which is designed to be fixed to the end of the crankshaft, which rotates relative to each other around the rotation axis, and a second inertia flywheel;

- damping means for transmitting torque between said first inertia flywheel and said second inertia flywheel and damping rotational non-periodicity, characterized in that during angular displacement between said first inertia flywheel and said second inertia flywheel, said first inertia flywheel And a friction member arranged to apply a frictional resistance torque between the first inertia flywheel and the second inertia flywheel. The present invention relates to a double damping flywheel for an automobile,

Characterized in that the double damping flywheel comprises an elastic thin plate, the damping means comprising a cam surface and rotating integrally with one of the first inertia flywheel and the second inertia flywheel; Wherein the double damping flywheel comprises a cam follower provided on the other of the first inertia flywheel and the second inertia flywheel and arranged to cooperate with the cam surface;

The angular displacement between the first inertia flywheel and the second inertia flywheel relative to the stop angle position causes the cam follower to apply a bending load to the resilient thin plate to move the first inertia flywheel and the second inertia flywheel to the non- And the cam surface is disposed so as to generate a reaction force capable of returning toward the second cam surface.

This requires a limited number of parts compared to a dual damping flywheel with a helical spring, so that the double damping flywheel is simple to manufacture and assemble.

In addition, the damping means is less sensitive to centrifugal force than the spiral spring of the prior art, so that the vibration damping performance is only marginally influenced by the centrifugal force.

In addition, the structure of such a double-damping flywheel can obtain a large relative clearance, and damping means having a limited rigidity can be used, thereby improving the efficiency.

On the other hand, the double damping flywheel may have a characteristic curve showing the change of the transmission torque according to the angular displacement, which indicates a discontinuous or inclined change without inflection point. As a result, the characteristic curve does not have an abrupt stiffness change zone which causes shocks and discontinuities which are detrimental to the damping performance.

Finally, since the cam surface is provided in the resilient thin plate, the manufacture of the double damping flywheel according to the present invention can be standardized in part. Indeed, if the characteristics of the double damping flywheel should be matched to the characteristics of the intended application, then only the shape and properties of the resilient thin plate may be matched.

According to another advantageous embodiment, such a dual damping flywheel may have one or more of the following features:

The cam follower is a wheel mounted to rotate on the other one of the first inertia flywheel and the second inertia flywheel.

The wheel is installed to rotate on the other one of the first inertia flywheel and the second inertia flywheel via a rolling bearing.

Said double damping flywheel comprising a second resilient thin plate provided with a cam surface and a second cam follower arranged cooperating with a cam surface of said second resilient thin plate, Lt; / RTI >

The first and second resilient thin plates are supported by the annular body.

The first and second resilient thin plates are each independently integral with one of the first inertia flywheel and the second inertia flywheel.

The double damping flywheel includes third and fourth resilient thin plates provided with cam surfaces and third and fourth cam followers disposed cooperatively with the cam surfaces of the third and fourth resilient thin plates, respectively.

The third and fourth resilient thin plates are supported by a second annular body and are symmetrical with respect to the rotation axis X and the second annular body extends axially along the length of the rotation axis X, As shown in Fig.

The third and fourth resilient thin plates are offset at an angle of 90 ° with respect to the first and second resilient thin plates.

The cam followers are radially arranged outside the resilient thin plate.

The cam surface is formed at the free end of the resilient thin plate.

The elastic thin plate includes a curved portion extending in the circumferential direction, and the cam surface is formed at the free end thereof.

The elastic foil being supported by an annular body fixed to the first inertial flywheel, the cam follower being supported by a rod extending between the second inertial flywheel and the wing, the second inertial flywheel and the wing And extend from both sides of the annular body.

The first flywheel comprises a radially inner hub for supporting a centering bearing of the second inertia flywheel on the first inertia flywheel and a radially inner hub extending radially beyond the centering bearing of the second inertia flywheel, And an annular portion having an orifice passing a screw for fixing the double damping flywheel to the nose, wherein the annular body supporting the resilient thin plate is provided with a screw for fixing a double damping flywheel to the nose of the crankshaft An orifice is provided.

The resilient thin plate is supported by an annular body integral with the second flywheel and the first flywheel comprises a radially inner hub supporting a rolling bearing for centering the second inertia flywheel relative to the first inertia flywheel Wherein the rolling bearing includes an inner ring cooperating with the radially inner hub and an outer ring being tightened between the annular body supporting the resilient thin plate and the second inertia flywheel.

The friction member comprises a first friction washer which can be driven to rotate by one of the first inertia flywheel and the second inertia flywheel and a second friction washer which is driven to rotate by the other one of the first inertia flywheel and the second inertia flywheel, And a "Belleville" elastic washer disposed to apply a pressure load of the first friction washer to the second friction washer.

The double damping flywheel includes a stop at the end of the course that can limit the relative angular displacement between the first inertial flywheel and the second inertial flywheel.

BRIEF DESCRIPTION OF THE DRAWINGS The present invention will be better understood by reference to the following detailed description of some specific embodiments of the invention, which are presented by way of non-limiting examples only with reference to the accompanying drawings, and other objects, details, features and advantages of the invention will become apparent will be.

1 is a front view of a double damping flywheel which shows the second inertia flywheel in a transparent manner so that the damping means is seen;
2 is a cross-sectional view of the double damping flywheel of FIG. 1 according to II-II.
3 is a perspective view of the double damping flywheel of FIG. 1;
- Figure 4 is a perspective view of the double damping flywheel of Figures 1 to 3, partially removed from the second inertial flywheel and disassembled from the first inertial flywheel.
5 is a front view of the double damping flywheel according to the second embodiment, showing the second inertia flywheel in a transparent manner so that the damping means can be seen;
6 is a cross-sectional view of the dual damping flywheel of FIG. 5 according to VI-VI.
7 is a partially broken perspective view of the dual damping flywheel of FIGS. 5 and 6. FIG.
8 is a front view of a dual damping flywheel according to a third embodiment showing the second inertia flywheel in a transparent manner so that the damping means can be seen;
9 is a cross-sectional view of the dual damping flywheel of FIG. 8 according to VIII-VIII;
10 is a partially broken perspective view of the dual damping flywheel of FIGS. 8 and 9. FIG.
- Fig. 11 is an example of a characteristic curve of a double damping flywheel showing transmission torque according to angular displacement.
12 is a schematic view of a damping means with a foil, showing the bending of the foil during angular displacement between the first and second inertia flywheels in the positive direction;
13 is a schematic view of a damping means with a foil, showing the bending of the foil during angular displacement between the first and second inertia flywheels in the reverse direction;
14 is a front view of a dual damping flywheel according to a fourth embodiment that does not show a portion of the second inertia flywheel so that the damping means and the saw tip of the course end are visible;
15 is a cross-sectional view of the dual damping flywheel of FIG. 14 according to XV-XV;
Figure 16 shows the double damping flywheel of Figure 14 in the stop position of the displacement end during the angular displacement of the second inertia flywheel relative to the first inertial flywheel in the reverse direction.
17 shows the means for forming the stopper of the displacement end according to the modified embodiment.
Figure 18 shows the double damping flywheel of Figure 14 in the stop position of the displacement end during angular displacement of the second inertia flywheel relative to the first inertial flywheel in the forward direction.
19 is a front view of a dual damping flywheel according to a fifth embodiment that does not show a portion of a second inertia flywheel so that the damping means can be seen;
20 is a cross-sectional view of the double damping flywheel of FIG. 19 according to XX-XX;

In the description and claims, the terms "inner" and "outer" and "axis" and "radial" directions are used to refer to elements of a dual damping flywheel, in accordance with the definitions set forth in the detailed description. Direction is a direction extending from the inside to the outside of the axis X perpendicular to the rotational axis X of the double damping flywheel which determines the "axis" direction, and the "circumferential" direction is a double damping flywheel And is orthogonal to the radial direction. The terms "outer" and "inner" are used to define, relative to another element, the relative position of one element with respect to the axis of rotation X of the double-damping flywheel, In contrast to the external elements.

First, reference is made to Figs. 1 to 4 showing the double damping flywheel 1 according to the first embodiment. The double damping flywheel 1 is guided to the first flywheel 2 by a first inertia flywheel 2 designed to be fixed at the end of a crankshaft of an internal combustion engine not shown and a ball rolling bearing 4 And a second inertia flywheel 3 that is centered. The second flywheel 3 is designed to form a reaction plate of a clutch (not shown) connected to the input shaft of the gearbox. The first inertia flywheel 2 and the second inertia flywheel 3 are installed to move around the rotation axis X and also rotate about the axis X relative to each other.

The first flywheel 2 comprises a radially inner hub 5 supporting a rolling bearing 4, a radially extending annular portion 6 and an annular portion 6 extending from the outer periphery of the annular portion 6 on the opposite side of the engine And a cylindrical portion 7 extending in the axial direction. The annular portion 6 is provided with an orifice through which a setscrew 8 for fixing the first flywheel 2 passes on the one hand and a damping means on the other hand on the first flywheel 2 An orifice through which the rivet (9) for fixing is passed is provided. The first flywheel 2 has a sawtooth crown 10 for rotating the first flywheel 2 by a starter on its outer periphery.

The radially inner hub 5 of the first flywheel includes a shoulder 11 which serves to bear the inner ring of the rolling bearing 5 and to hold the inner ring in the direction of the engine. Likewise, the second flywheel 3 includes a shoulder portion 12, which surrounds the outer ring of the rolling bearing 5 and serves to hold the outer ring in the opposite direction of the engine.

The second flywheel 3 includes an annular flat surface 13 facing away from the first flywheel 2, forming a support surface for a friction lining of a clutch disc, not shown. The second flywheel 3 includes a terminal 14 and an orifice 15 for the installation of the cover of the clutch, near its outer edge. The second flywheel 3 further includes an orifice 16 through which the screw 8 is passed during installation of the double damping flywheel 1 on the crankshaft and facing the orifice formed in the first flywheel 2 .

The first flywheel 2 and the second flywheel 3 are rotationally connected by damping means. In the embodiment shown in Figs. 1 to 4, these damping means include two resilient thin plates 17a and 17b installed to rotate integrally with the first flywheel 2. The elastic thin plates 17a and 17b are supported by an annular body 18 provided with an orifice through which the fixed rivet 9 with respect to the first flywheel 2 can pass. The annular body 18 further comprises an orifice 19 for passing a screw 8 for securing the double damping flywheel 1 to the nose of the crankshaft. The two elastic thin plates 17a and 17b are symmetrical with respect to the rotational axis X of the clutch disc.

The elastic thin plates 17a and 17b are provided at one free end with a cam surface 20 arranged to cooperate with a cam follower provided in the second flywheel 3. The elastic thin plates 17a and 17b include curved portions extending substantially in the circumferential direction. The radius of curvature of the curved portion and the length of the curved portion are determined according to the desired rigidity of the elastic thin plates 17a and 17b. The elastic thin plates 17a and 17b may be formed as a single member or a plurality of thin layers arranged axially with respect to each other.

The cam follower is a wheel 21 supported by a second rod 3 on the one hand and a cylindrical rod 22 securing the wing 23 on the other hand. The wheel 21 is installed to rotate on the cylindrical rod 22 about a rotation axis X parallel to the rotation axis X. [ The wheels 21 are held to be supported against respective cam faces 20 and are arranged to roll against the cam faces 20 during relative movement between the first flywheel 2 and the second flywheel 3 do. The wheel 21 is disposed radially outwardly of each cam face 20 so as to keep the elastic thin plates 17a and 17b in a radial direction when receiving centrifugal force. Advantageously, the wheel 21 is mounted to rotate on a cylindrical rod via a rolling bearing, in a manner that reduces collateral friction that can affect the damping function. For example, the rolling bearing may be a ball bearing or a roller. In one embodiment, the wheel 21 has an anti-friction coating.

The cam surface 20 is configured such that the wheel 21 is displaced on the cam surface 20 with respect to the angular displacement between the first flywheel 2 and the second flywheel 3 with respect to the non- And is arranged to apply a bending load to the elastic thin plates 17a and 17b. The elastic thin plates 17a and 17b apply a restoring force to the wheel 21 and the restoring force causes the first flywheel 2 and the second flywheel 3 to return toward their relative non- . The elastic thin plates 17a and 17b can transmit the driving torque of the first flywheel 2 to the second flywheel 3 and the drive torque of the second flywheel 3 to the first flywheel 3 ) (Reverse direction).

The working principle of the damping means for the elastic thin plates 17a and 17b will be described in detail with reference to Figs. 12 and 13. Fig.

The transmitted torque is transmitted along the first direction between the first flywheel 2 and the second flywheel 3 when the drive engine torque is transmitted from the first flywheel 2 toward the second flywheel 3 (See FIG. 12). Therefore, the wheel 21 is displaced at an angle with respect to the elastic thin plate 17a. The displacement of the wheel 21 on the cam surface 20 causes the elastic thin plate 17a to bend in the direction of the arrow A direction. In order to show the bending of the elastic thin plate 17a, the elastic thin plate 17a is shown as a solid line at the stop angle position and a dotted line at the angular displacement.

The bending load P is particularly dependent on the geometry of the resilient thin plate 17a and its material, particularly its lateral elastic modulus. The bending load P is decomposed into a radial component Pr and a tangential component Pt. The tangential component (Pt) enables transmission of the engine torque. In the reaction, the resilient foil 17a applies a reaction force to the wheel 21 and the tangential component of the reaction force causes the first flywheel 2 and the second flywheel 3 to return toward their relative non- The restoring force that can be made.

When the resistance torque is transmitted from the second flywheel 3 to the first flywheel 2 (reverse direction), the transmitted torque is transmitted to the first flywheel 2 and the second flywheel 3 (See FIG. 13). Therefore, the wheel 21 is displaced at an angle of? With respect to the resilient thin plate 17a. In this case, the tangential component Pt of the bending load has an opposite direction to the tangential component of the bending load shown in Fig. Likewise, the elastic thin plate 17a applies a reaction force in the direction opposite to that shown in Fig. 12 so that the first flywheel 2 and the second flywheel 3 return toward their relative stopping angular positions.

The irregularity of the torque generated by the internal combustion engine and the torsional vibration are transmitted to the first flywheel 2 by the crankshaft to cause a relative rotation between the first flywheel 2 and the second flywheel 3. These vibrations and irregularities are attenuated by the bending of the elastic thin plate 17a.

Referring again to Figures 1-4, the damping means includes a friction member arranged to apply a resistance torque therebetween during the relative clearance of the first flywheel 2 and the second flywheel 3. Thereby, the friction member can dissipate the energy accumulated in the elastic thin plates 17a and 17b. The friction member includes a "Belleville" washer-type elastic washer 24, a first friction washer 25 that rotates integrally with the first flywheel 2, and a first friction washer 25 that rotates integrally with the first flywheel 2, And a second friction washer 26 that can be rotationally driven relative to the first flywheel 2 during relative clearance. The elastic washer 24 is interposed between the first flywheel 2 and the first friction washer 25 to ensure the pressure load of the first friction washer 25 against the second friction washer 26 do. The first friction washer 25 is rotated integrally with the first flywheel 2 by the axial fingers shown in FIG. 2 inserted into the opening provided in the first flywheel 2. The second friction washer 26 has, on the outer periphery thereof, a toothed portion which engages with a toothed portion formed in the inner periphery of the vane 23 with a predetermined circumferential clearance. Thereby, during the clearance between the first flywheel 2 and the second flywheel 3, when the circumferential clearance is compensated, the second friction washer 26 is rotationally engaged with the second flywheel 3 The friction torque acts between the first and second friction washers 25, 26.

5 to 7 show a double damping flywheel 1 according to a second embodiment. In this embodiment, the first flywheel 2 includes a radially inner hub 5 that supports the centering bearing 4 of the second flywheel 3, which includes a double damping flywheel 1 in the nose of the crankshaft An orifice 27 for passing a screw for fixing is provided.

The damping means includes two resilient thin plates 17a and 17b which are installed to rotate integrally with the second flywheel 3 and cooperate with a cam follower provided on the first flywheel 2, As shown in FIG. The elastic thin plates 17a and 17b are supported by the annular body 18. The annular body 18 is fixed to the first flywheel 2 via a plurality of rivets 28 cooperating with the annular body 18 and an orifice provided in the first flywheel 2.

The radially inner hub 5 of the first flywheel 2 includes a shoulder 11 which serves to support the inner ring of the rolling bearing 5 and holds the inner ring in the direction of the engine. The outer ring of the rolling bearing 5 is tightened between the annular body 18 supporting the elastic thin plates 17a and 17b and the second flywheel 3. To this end, the annular body 18 has a shoulder portion 30 for holding the outer ring in the engine direction, and the second flywheel 3 has, on its inner periphery, And a shoulder portion 31 for holding the ring in the direction opposite to the engine.

The cam follower is a wheel 21 provided to rotate on the first flywheel 2 around an axis parallel to the rotation axis X. [ The wheel 21 is installed on a cylindrical rod 22 fixed to the first flywheel 2 via a rolling bearing.

On the other hand, the damping means of the double damping flywheel of FIGS. 5 to 7 also includes a friction member arranged to apply a resistance torque therebetween during the relative clearance of the first flywheel 2 and the second flywheel 3 do. The friction member includes a "Belleville-type" elastic washer 32, a first friction washer 33 rotating integrally with the first flywheel 2, and a second friction washer 33 rotating relative to the first flywheel 2 and the second flywheel 3, And a second friction washer (34) rotatable relative to the first flywheel (2) during clearance. The elastic washer 32 is fixed in a direction opposite to the engine in the axial direction by a standing clip. The elastic washer 32 tightens the second friction washer 34 between the first friction washer 33 and the first flywheel 2 by applying an axial load to the first friction washer 33 . The first friction washer 33 has a leg cooperating with a groove provided on the outer periphery of the hub 5 of the first flywheel 2 so as to surround the first friction washer 33 Thereby rotating the first flywheel 2 integrally. The second friction washer 34 is provided on its outer periphery with a lid 28 cooperating with the head of the rivet 28 which fixes the annular body 18 to the second flywheel 3 with a predetermined circumferential spacing And permits the relative movement of the second friction washer 34 with respect to the first flywheel 2 during the relative clearance of the first flywheel 2 and the second flywheel 3.

8 to 10 show a double damping flywheel 1 according to a third embodiment. This double damping flywheel 1 is substantially similar to the double damping flywheel 1 of Figs. 5-7, except that the damping means comprises two pairs of resilient thin plates 17a, 17b, 17c and 17d. The first pair of resilient thin plates 17a and 17b are supported on the first annular body 18 and the second pair of resilient thin plates 17c and 17d are supported on the second annular body 18. [ The elastic thin plates 17a, 17b, 17c and 17d are symmetrical with respect to the rotation axis X for each pair. The first and second annular bodies 18 are secured to the second flywheel 3 via a plurality of rivets 28. In which a spacer ring 35 is axially disposed between the first and second annular bodies 18.

In the illustrated embodiment, the two annular bodies 18 and the two pairs of resilient thin plates 17a, 17b, 17c and 17d are identical. One of the elastic thin plates 17a, 17b, 17c and 17d of the pair of elastic thin plates is offset at an angle of 90 DEG with respect to the other pair of elastic thin plates. This arrangement can distribute the load applied to the rolling bearing 4 more uniformly.

The cam follower here includes two pairs of wheels 21 mounted for rotation on a cylindrical rod 22 fixed to the first flywheel 2.

14 to 18 show a double-damping flywheel 1 according to a fourth embodiment. This double damping flywheel 1 is substantially similar to the double damping flywheel 1 of Figures 5 to 7 but has a course end which can limit the relative angular displacement between the first flywheel 2 and the second flywheel 3. [ And stoppers 36 and 37 of the stoppers 36 and 37, respectively. Such a stopper can transmit torque between the first inertia flywheel 2 and the second inertia flywheel 3 when the damping means is broken, or when the excess torque is transmitted due to a malfunction of the power train or a limited use condition The damping means can be protected.

In the illustrated embodiment, the stoppers 36 and 37 comprise a first inertia flywheel 2 and a protruding element formed in the weight of the second inertia flywheel 3. Alternatively, the stoppers 36 and 37 may be composed of a first inertia flywheel 2 and an accessory member on the second inertia flywheel 3, for example, by riveting.

In the embodiment of Figures 14, 15, 16 and 18, each of the first inertia flywheels includes two stoppers 36, 37 diametrically opposed. Therefore, these stoppers 36 and 37 act in two directions. When the second inertia flywheel 3 relatively rotates in the reverse direction R with respect to the first inertia flywheel 2, the first supporting surface of the stopper 37 provided in the second flywheel 3 Is supported on the first support surface of the stopper 36 provided in the first flywheel 2 as shown in FIG. On the other hand, when the second inertia flywheel 3 relatively rotates in the forward direction D with respect to the first inertia flywheel 2, the second inertia flywheel 3 rotates about the second support of the stopper 37 provided on the second flywheel 3, 18 is supported on the second supporting surface of the stopper 36 provided in the first flywheel 2 as shown in Fig.

17, a stop of a course end is formed by supporting the resilient thin plate 17b on the stopper surface 38 provided in the annular body 18 or by another resilient thin plate 17a. In this case, the cam surface 20 of the resilient thin plates 17a and 17b is disposed such that the resilient thin plate 17a is supported on the stopper surface 38 with respect to a given relative angular displacement.

19 and 20 show the double damping flywheel 1 according to the fifth embodiment. This double damping flywheel 1 is also similar to the double damping flywheel disclosed in connection with Figs. 5-7. However, this dual damping flywheel differs in that it includes two resilient thin plates independently attached to the first inertial flywheel 2, as in Figures 19 and 20, or to the second inertial flywheel 3 not shown . The elastic thin plates 17a and 17b are fixed to the first inertial weight 2 by the rivet 39 here. This arrangement can simplify the production of the elastic thin plates 17a and 17b.

11 shows a characteristic curve of the double damping flywheel 1 implemented in accordance with the teachings of the present invention. This characteristic curve represents a transmission torque expressed by 'N.m' according to the angular displacement indicated by 'degrees'. The relative clearance between the input and output elements in the forward direction is shown in dashed lines while the reverse play is shown in solid lines. With this double-damping flywheel 1, it is possible to obtain a damping characteristic curve in which the gradient gradually changes without discontinuity.

Advantageously, the cam surface 20 and the resilient thin plates 17a, 17b, 17c and 17d are arranged such that the characteristic function of the transmission torque according to the angular displacement is a monotonic function.

In some applications, the cam surface 20 and the resilient thin plates 17a, 17b, 17c, 17d may be arranged such that the characteristic function of the transmission torque according to the angular displacement in the opposite direction and in the normal direction is symmetrical with respect to the non-stationary position.

While the invention has been described in connection with certain specific embodiments thereof, it will be understood that it is not intended to be exhaustive or to limit the invention to the precise form disclosed and that all such modifications are intended to be included within the scope of the present invention.

The use of the word "includes " and variations thereof does not exclude the presence of elements or steps other than those listed in a claim. The use of the singular representation of an element or step does not exclude the presence of a plurality of such elements or steps, unless otherwise stated.

In the claims, all the signs in parentheses are not to be construed as limiting the claim.

Claims (17)

  1. A first inertia flywheel 2 and a second inertia flywheel 3, which are designed to be fixed at the ends of the crankshaft, which rotate about each other about the rotation axis X;
    - damping means for transmitting torque between said first inertia flywheel (2) and said second inertia flywheel (3) and damping rotational non-periodicity, characterized in that said first inertia flywheel (2) and said second inertia flywheel (24, 25, 26; 32, 33, 34) arranged to apply frictional resistance torque between the first inertia flywheel (2) and the second inertia flywheel (3) during angular displacement between the first inertia flywheel A damping flywheel (1) for a motor vehicle, comprising a damping means
    The double-damping flywheel 1 includes elastic thin plates 17a, 17b, 17c, and 17d, which are integrally rotated with one of the first inertia flywheel 2 and the second inertia flywheel 3 and provided with the cam surface 20, Characterized in that the damping means comprises: The double damping flywheel includes a cam follower (21) disposed on the other of the first inertia flywheel (2) and the second inertia flywheel (3) and arranged to cooperate with the cam surface (20);
    17b, 17c, 17d) against the angular displacement between the first inertia flywheel (2) and the second inertia flywheel (3) with respect to the stop angle position, the cam follower (21) Wherein the cam surface (20) is arranged to generate a reaction force capable of returning the first inertia flywheel (2) and the second inertia flywheel (3) toward the stop angle position.
    Double damping flywheel.
  2. The method according to claim 1,
    Characterized in that the cam follower is a wheel (21) provided to rotate on the other one of the first inertia flywheel (2) and the second inertia flywheel (3)
    Double damping flywheel.
  3. 3. The method of claim 2,
    Characterized in that the wheel (21) is installed to rotate on the other one of the first inertia flywheel (2) and the second inertia flywheel (3) via a rolling bearing
    Double damping flywheel.
  4. 4. The method according to any one of claims 1 to 3,
    A second cam follower 20 arranged to cooperate with the second resilient thin plates 17a, 17b, 17c and 17d provided with the cam face 20 and the cam face 20 of the second resilient thin plates 17a, 17b, 17c and 17d, Characterized in that the first and second elastic thin plates (17a, 17b, 17c, 17d) are symmetrical with respect to the rotation axis (X)
    Double damping flywheel.
  5. 5. The method of claim 4,
    Characterized in that the first and second resilient thin plates (17a, 17b, 17c, 17d) are supported by an annular body
    Double damping flywheel.
  6. 5. The method of claim 4,
    Characterized in that the first and second resilient thin plates (17a, 17b) are independently integrated with one of the first inertia flywheel (2) and the second inertia flywheel (3)
    Double damping flywheel.
  7. 6. The method of claim 5,
    Third and fourth cams arranged to cooperate with the third and fourth elastic thin plates 17a, 17b, 17c and 17d provided with the cam face 20 and the cam face 20 of the third and fourth elastic thin plates, Characterized in that it comprises a follower (21)
    Double damping flywheel.
  8. 8. The method of claim 7,
    The third and fourth resilient thin plates 17a, 17b, 17c and 17d are supported by a second annular body 18 and are symmetrical with respect to the rotation axis X, Is offset with respect to the first annular body (18) in the axial direction along the length of the first annular body (X)
    Double damping flywheel.
  9. 9. The method of claim 8,
    Wherein the third and fourth elastic thin plates 17a and 17b are offset at an angle of 90 degrees with respect to the first and second elastic thin plates 17c and 17d.
    Double damping flywheel.
  10. 10. The method according to any one of claims 1 to 9,
    Characterized in that the cam followers (21) are radially arranged outside the elastic thin plates (17a, 17b; 17c, 17d)
    Double damping flywheel.
  11. 11. The method according to any one of claims 1 to 10,
    Characterized in that the cam surface (20) is formed at the free end of the elastic thin plates (17a, 17b; 17c, 17d)
    Double damping flywheel.
  12. 12. The method of claim 11,
    Characterized in that the elastic thin plates (17a, 17b; 17c, 17d) include a curved portion extending in the circumferential direction and the cam surface (20) is formed at the free end thereof
    Double damping flywheel.
  13. 13. The method according to any one of claims 1 to 12,
    The elastic thin plates 17a and 17b are supported by an annular body 18 fixed to the first inertia flywheel 2 and the cam followers 21 are supported by the second inertia flywheel 3 Characterized in that the second inertia flywheel (3) and the wing (23) extend on both sides of the annular body (18)
    Double damping flywheel.
  14. 14. The method of claim 13,
    The first inertia flywheel 2 includes a radially inner hub 5 supporting the centering bearing 4 of the second inertia flywheel 3 on the first inertia flywheel 2, , And an annular portion (6) having an orifice extending in the radial direction beyond the flange portion and passing a screw (9) for fixing the double damping flywheel (1) to the nose of the crankshaft of the engine, wherein the resilient thin plate 17b, 17c, 17d) is provided with an orifice (19) for passing a screw (9) for fixing the double damping flywheel (1) to the nose of the crankshaft
    Double damping flywheel.
  15. 15. The method according to any one of claims 1 to 14,
    The elastic thin plates 17a and 17b are supported by an annular body 18 integral with the second flywheel 3 and the first flywheel 2 is supported by the first inertia flywheel 2 (5) supporting a rolling bearing (5) for centering said second inertia flywheel (3) with respect to said radial inner hub (5), said rolling bearing (5) Characterized in that it comprises an inner ring and an outer ring which is tightened between the annular body (18) bearing the elastic thin plates (17a, 17b; 17c, 17d) and the second inertia flywheel (3)
    Double damping flywheel.
  16. 16. The method according to any one of claims 1 to 15,
    The friction member includes a first friction washer (24, 32) rotatably driven by one of the first inertia flywheel (2) and the second inertia flywheel (3) And a second friction washer (25, 34) rotatable by another one of the second inertia flywheel (3), and a second friction washer (25, 34) Characterized in that it comprises a "Belleville" type elastic washer (24, 32) arranged to apply a pressure load of <
    Double damping flywheel.
  17. 17. The method according to any one of claims 1 to 16,
    And stoppers (36, 37) at the end of the course that can limit the relative angular displacement between the first inertia flywheel (2) and the second inertia flywheel (3)
    Double damping flywheel.
KR1020140083683A 2013-07-08 2014-07-04 Double damping flywheel with improved damping means KR20150006366A (en)

Priority Applications (2)

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FR1356687 2013-07-08
FR1356687A FR3008152B1 (en) 2013-07-08 2013-07-08 Double flywheel damper with improved amortization means

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KR20150006366A true KR20150006366A (en) 2015-01-16

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CN104279268B (en) 2018-11-16
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FR3008152B1 (en) 2015-08-28
EP2824361B1 (en) 2018-07-18
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FR3008152A1 (en) 2015-01-09
CN104279268A (en) 2015-01-14

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